Discharge valve and compressor having the same

ABSTRACT

Disclosed herein are a discharge valve and a compressor having the same. The discharge valve includes a valve casing having a hook formed around the upper portion thereof such that the hook is seated on a discharge port of a cylinder block, a first opening formed at the center of the upper portion for introduction of a compressed fluid, and a second opening formed around the lower portion thereof for discharge of the compressed fluid, a core body disposed within the valve casing, an elastic body disposed to touch one side of the core body, and a support block mounted to the lower end of the valve casing to support the elastic body. According to the disclosure, the separation of the discharge valve can be prevented due to back pressure between a discharge pipe and the inside of the compressor by pressing the discharge valve against a discharge gasket.

TECHNICAL FIELD

The present disclosure relates to a discharge valve and a compressor having the same, and more particularly, to a discharge valve that can be prevented from being separated due to back pressure by pressing the discharge valve against a discharge gasket, and a compressor having the same.

BACKGROUND ART

In general, a compressor serving to compress a refrigerant in a vehicle cooling system has been developed in various forms. Examples of the compressor include a reciprocating compressor configured such that its component compresses a refrigerant while reciprocating, and a rotary compressor configured such that its component compresses a refrigerant while rotating.

Here, examples of the reciprocating compressor include a crank compressor that transmits driving force from a drive source to a plurality of pistons using a crank, a swash plate compressor that transmits driving force from a drive source to a rotary shaft having a swash plate installed thereto, and a wobble plate compressor that uses a wobble plate. Examples of the rotary compressor include a vane rotary compressor that uses a rotary shaft and a vane, and a scroll compressor that uses an orbiting scroll and a fixed scroll.

Meanwhile, examples of the swash plate compressor include a fixed-capacity swash plate compressor, in which the installation angle of a swash plate is fixed, and a variable-capacity swash plate compressor capable of changing a discharge capacity by changing the angle of inclination of a swash plate.

FIG. 1 illustrates an example of a typical swash plate compressor. The configuration of the swash plate compressor will be schematically described below with reference to FIG. 1.

The swash plate compressor 10 (hereinafter, referred to as “compressor”) includes a cylinder block 20 defining a portion of the external appearance and frame thereof. In this case, a center bore 21 is formed through the center of the cylinder block 20, and a rotary shaft 60 is rotatably installed in the center bore 21.

A plurality of cylinder bores 22 is formed through the cylinder block 20 to radially surround the center bore 21, and a piston 70 is installed in each of the cylinder bores 22 so as to be capable of rectilinearly reciprocating. In this case, the piston 70 has a cylindrical shape, the cylinder bore 22 is a cylindrical space corresponding thereto, and the refrigerant in the cylinder bore 22 is compressed by the reciprocating motion of the piston 70.

A front housing 30 is coupled to the front of the cylinder block 20. The front housing 30 forms a crank chamber 31 therein together with the cylinder block 20 by tensioning the surface of the front housing 30 facing the cylinder block 20.

A pulley 32, which is connected to an external power source (not shown) such as an engine, is rotatably installed in front of the front housing 30, and the rotary shaft 60 rotates along with the rotation of the pulley 32.

A rear housing 40 is coupled to the rear of the cylinder block 20. In this case, discharge chambers 41 are formed in the rear housing 40 along a portion adjacent to the outer peripheral edge of the rear housing 40 to selectively communicate with the cylinder bores 22.

An inlet 43 and a suction chamber 42, in which the fluid sucked thereinto stays, are installed at any positions of the rear housing 40, but they may also be installed at different positions according to the type of the compressor. That is, their installation is not necessarily limited to the above positions.

In this case, a discharge gasket 50 is interposed between the cylinder block 20 and the rear housing 40, and each of the discharge chambers 41 communicates with an associated one of the cylinder bores 22 through a discharge port 51 formed in the discharge gasket 50.

In addition, a swash plate 61 is installed on the rotary shaft 60. The swash plate 61 is connected to the individual pistons 70 by shoes 62 arranged along the edge of the swash plate 61, and the pistons 70 rectilinearly reciprocate in the cylinder bores 22 by the rotation of the swash plate 61.

In this case, the swash plate 61 is installed such that the angle thereof to the rotary shaft 60 is variable, thereby enabling the discharge amount of refrigerant in the compressor 10 to be regulated. To this end, the opening degree of a passage, which allows the discharge chamber 41 to communicate with the crank chamber 31, is adjusted by a pressure regulation valve (not shown).

The conventional swash plate compressor having the above configuration has a so-called radial symmetry structure in which the cylinder bores 22 formed in the cylinder block 20 are radially spaced about the rotary shaft 60,

FIG. 2 is a cross-sectional view illustrating an example of a conventional rear housing 40. In this example, discharge chambers 41 are arranged along the outer circumference of the rear housing 40 and a suction chamber 42 is disposed in the center of the rear housing 40. A suction check valve 80 is mounted to the suction chamber 42. When a constant hydraulic pressure is generated in the suction chamber 42, a fluid is introduced thereinto while a core 81 of the suction check valve 80 is pushed, whereas when the hydraulic pressure is lowered again, an inlet 43 is closed while the core 81 moves forward again by the elastic force of a spring 82.

A discharge valve 90 is disposed on each of the discharge chambers 41. The discharge valve 90 is provided to prevent a compressed fluid from flowing backward toward the discharge chamber 41 due to a difference in pressure when a compressor is stopped after the compressed fluid is introduced into a discharge pipe.

In addition, the discharge valve 90 allows the pressure of a compressed fluid to be kept relatively uniform when the compressed fluid is discharged, thereby bringing about an effect of relieving noise and vibration when the compressor operates.

FIG. 3 is a view illustrating an example of an existing discharge valve 90. The conventional discharge valve 90 is press-fitted to a fluid outlet 45 in a discharge chamber 41. Thus, the discharge valve 90 has a press-fitting portion 91 made of a metal material such as copper or aluminum, and is fixed by forcibly press-fitting the press-fitting portion 91 to a stepped portion 46.

One side of the press-fitting portion 91 is connected to a valve body 92, and the valve body 92 has an opening 93 formed thereon. Thus, the discharge valve 90 has a structure in which a compressed air flows toward the outlet 45 through the opening 93 while a core (not shown) is pushed rearward by the discharge hydraulic pressure of the compressed air. Of course, the core is closed by moving forward again when the discharge hydraulic pressure is lowered since the discharge valve 90 has a spring (not shown) therein.

In recent years, a reduction in cost has tended to be continuously required according to economical environment such as customer's needs or material cost rise. Accordingly, there is a need for the structure of the discharge valve 90, which is capable of further reducing costs by eliminating the press-fitting portion 91, made of a metal material, therefrom while the discharge valve 90 is stably fixed to the outlet 45 to enable the function of the discharge valve 90 to be performed.

DISCLOSURE Technical Problem

The present disclosure has been made in view of the above-mentioned problems, and an object thereof is to provide a discharge valve that can be prevented from being separated due to back pressure by pressing the discharge valve against a discharge gasket, and a compressor having the same.

Technical Solution

In order to accomplish the above object, the present disclosure provides a discharge valve and a compressor having the same. In accordance with one aspect of the present disclosure, a discharge valve for compressors includes a valve casing having a hook formed around one side thereof such that the hook is seated on a discharge port of a rear housing, a first opening formed at a center of the one side for introduction of a compressed fluid, and a second opening formed around the other side thereof for discharge of the compressed fluid, a core body disposed within the valve casing, an elastic body disposed to touch one side of the core body, and a support block mounted to the other side of the valve casing to support the elastic body.

In the aspect of the present disclosure, the hook may include a first hook disposed around the one side of the valve casing, and a second hook disposed around the one side of the valve casing at a position facing the first hook.

In the aspect of the present disclosure, the first hook may have a greater length than the second hook.

In the aspect of the present disclosure, the first and second hooks may have different length.

In the aspect of the present disclosure, the first hook may include a first piece having a flat inner surface and a round outer surface, and a first support bar disposed between one surface of the valve casing and an inner surface of the first piece to support the first piece.

In the aspect of the present disclosure, the second hook may include a second piece having a flat inner surface and a round outer surface, and a second support bar disposed between one surface of the valve casing and an inner surface of the second piece to support the second piece.

In the aspect of the present disclosure, the discharge valve may further include a recessed groove formed along a central circumference of the valve casing, and a sealing unit disposed in the recessed groove to be pressed against an inner surface of the outlet.

In the aspect of the present disclosure, the valve casing, the core body, and the support block may be made of plastic.

In accordance with another aspect of the present disclosure, a compressor includes a valve plate provided with a discharge gasket having a discharge port through which a compressed fluid is discharged, a rear housing connected to the valve plate and having a discharge chamber connected to the discharge port, and a discharge valve disposed on the discharge chamber and including first and second hooks having different lengths corresponding to the shape of the discharge gasket.

Advantageous Effects

In accordance with the present disclosure, it is possible to prevent separation of a discharge valve disposed at a discharge port, which may be caused by the back pressure between a discharge pipe and the inside of a compressor, by pressing one side of the discharge valve against a discharge gasket.

This fixing structure can also be made of a plastic material, and is to change a conventional method of fixing a discharge valve by press-fitting a component, which is made of a metal material such as copper or aluminum, to a discharge port. Therefore, it is possible to reduce product costs and simultaneously maintain a separation prevention function as in the related art.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a side cross-sectional view illustrating a swash plate compressor.

FIG. 2 is a view illustrating a discharge valve disposed at a discharge port in a conventional cylinder block

FIG. 3 is a view illustrating a fixed state of a conventional discharge valve.

FIG. 4 is a side view illustrating a discharge valve according to the present disclosure.

FIG. 5 is an exploded perspective view of the discharge valve illustrated in

FIG. 4.

FIG. 6 is a view illustrating a state in which the discharge valve of the present disclosure is mounted to a discharge port of a cylinder block.

FIG. 7 is a view illustrating a fixed state of the discharge valve according to the present disclosure.

BEST MODE FOR INVENTION

Hereinafter, a discharge valve and a compressor having the same according to exemplary embodiments of the present disclosure will be described in detail with reference to the accompanying drawings.

FIG. 4 is a side view illustrating a discharge valve according to the present disclosure. FIG. 5 is an exploded perspective view of the discharge valve illustrated in FIG. 4, FIG. 6 is a view illustrating a state in which the discharge valve of the present disclosure is mounted to a discharge port of a cylinder block, FIG. 7 is a view illustrating a fixed state of the discharge valve according to the present disclosure.

First, the basic structure of a swash plate compressor to which the present disclosure is applied will be described with reference to FIG. 1, However, the present disclosure is not necessarily limited to this structure, and the description of the swash plate compressor is valid only within bounds for understanding of the present disclosure.

Referring to FIG. 1, the swash plate compressor, which is designated by reference numeral 10, includes a cylinder block 20 defining a portion of the external appearance and frame thereof. In this case, a center bore 21 is formed through the center of the cylinder block 20, and a rotary shaft 60 is rotatably installed in the center bore 21.

A plurality of cylinder bores 22 is formed through the cylinder block 20 to radially surround the center bore 21, and a piston 70 is installed in each of the cylinder bores 22 so as to be capable of rectilinearly reciprocating. In this case, the piston 70 has a cylindrical shape, the cylinder bore 22 is a cylindrical space corresponding thereto, and the refrigerant in the cylinder bore 22 is compressed by the reciprocating motion of the piston 70.

A front housing 30 is coupled to the front of the cylinder block 20. The front housing 30 forms a crank chamber 31 therein together with the cylinder block 20 by tensioning the surface of the front housing 30 facing the cylinder block 20.

A pulley 32, which is connected to an external power source (not shown) such as an engine, is rotatably installed in front of the front housing 30, and the rotary shaft 60 rotates along with the rotation of the pulley 32.

A rear housing 800 is coupled to the rear of the cylinder block 20, as illustrated in FIGS. 6 and 7. The general external appearance of the rear housing 800 is similar to that of a rear housing 40 illustrated in FIG. 1, the present disclosure is necessarily limited thereto.

In this case, discharge chambers 810 (which are similar to those designated by reference numeral 41 of FIG. 2 but the present disclosure is not necessarily limited thereto) are formed in the rear housing 800 along a portion adjacent to the outer peripheral edge of the rear housing 800 to selectively communicate with the cylinder bores 22.

Referring to FIGS. 6 and 7, an inlet (not shown) is formed at one side of the rear housing 800, and is connected to a suction chamber (not shown; which is similar to that designated by reference numeral 42 of FIG. 2 but the present disclosure is not necessarily limited thereto) disposed at the center of the rear housing 800. However, the present disclosure is not necessarily limited thereto, and they may also be installed at different positions according to the type of the compressor.

In this case, a valve plate 50 is interposed between the cylinder block 20 and the rear housing 800, and each of the discharge chambers 810 communicates with an associated one of the cylinder bores 22 through a discharge port 51 formed in the valve plate 50.

In addition, a swash plate 61 is installed on the rotary shaft 60. The swash plate 61 is connected to the individual pistons 70 by shoes 62 arranged along the edge of the swash plate 61, and the pistons 70 rectilinearly reciprocate in the cylinder bores 22 by the rotation of the swash plate 61.

In this case, the swash plate 61 is installed such that the angle thereof to the rotary shaft 60 is variable, thereby enabling the discharge amount of refrigerant in the compressor 10 to be regulated. To this end, the opening degree of a passage, which allows the discharge chamber 810 to communicate with the crank chamber 31, is adjusted by a pressure regulation valve (not shown).

The conventional swash plate compressor having the above configuration has a so-called radial symmetry structure in which the cylinder bores 22 formed in the cylinder block 20 are radially spaced about the rotary shaft 60.

Through such a structure, when the swash plate 61 rotates, the pistons 70 are operated to compress a fluid, and the compressed fluid is pushed out to the discharge chamber 810 through the discharge port 51 of the valve plate 50 while a valve door 52 is opened by hydraulic pressure.

Hereinafter, a discharge valve for compressors according to the present disclosure will be described.

Referring to FIGS. 4 to 7, the discharge valve for compressors, which is designated by reference numeral 100, according to the present disclosure may include a valve casing 210, a core body 300, an elastic body 400, and a support block 500.

The valve casing 210, the core body 300, and the support block 500 may be made of a plastic material for cost reduction. The valve casing 210 may have a hook 211, 216 formed around one side 250 thereof such that the hook 211, 216 is seated on the discharge chamber 810 of the rear housing 800, and a first opening 230 formed at the center of the one side 250 thereof for introduction of a compressed fluid. The valve casing 210 may have a second opening 240 formed around the other side 260 thereof for discharge of the compressed fluid.

The core body 300 may be disposed in the other side 260 of the valve casing 210. The core body 30 is disposed in the state in which one end thereof touches the first opening 230 and the circumference thereof touches the second opening 240.

The core body 300 has an internal groove 310 formed in the other end thereof, and the elastic body 400 is inserted into the internal groove 310 for arrangement. Here, the elastic body 400 may be a coil spring, but the present disclosure is not necessarily limited thereto.

The support block 500 has a protrusion 510 formed at the center thereof. The protrusion 510 is inserted into the elastic body 400 for arrangement to support the elastic body 400 and functions to guide the extension and contraction direction of the elastic body 400. The support block 500 has an extension 520 extending radially from the outer circumference thereof. Thus, after the support block 500 is tightly fitted into the other side of the valve casing 210, the arrangement position of the support block 500 is fixed by a fixing piece 530.

The hook 211, 216 may include a first hook 211 disposed around the one side 250 of the valve casing 210, and a second hook 216 disposed around the one side 250 of the valve casing 210 at a position facing the first hook 211.

The first hook 211 may consist of a first piece 212 and a first support bar 213. The first piece 212 may have a flat inner surface and a round outer surface. The first support bar 213 is disposed between one surface of the valve casing 210 and the inner surface of the first piece 212 and functions to support the first piece 212.

The second hook 216 may consist of a second piece 217 and a second support bar 218. The second piece 217 may have a flat inner surface and a round outer surface. The second support bar 218 is disposed between one surface of the valve casing 210 and the inner surface of the second piece 217 and functions to support the second piece 217.

In an embodiment of the present disclosure, the first hook 211 may have a greater length than the second hook 216. This is to support one end of the second hook 216 by a discharge gasket 700.

Referring to FIGS. 6 and 7, a first round groove 860 and a second round groove 870 are formed on an outlet 850 in the discharge chamber 810 so as to correspond to the outer peripheral surfaces of the first and second pieces 212 and 217, and thus the valve casing 210 in inserted into the outlet 850 for arrangement.

The first hook 211 is positioned at the first round groove 860 formed in the outside of the discharge chamber 810 and the second hook 216 is positioned at the second round groove 870 formed in the inside of the discharge chamber 810. In this case, when the discharge gasket 700 is disposed at the upper portion of the discharge chamber 810, the discharge gasket 700 is seated on one end of the first hook 211, and a gasket block 710 forming a discharge port 720 is seated on one end of the second hook 216, as illustrated in FIG. 7. The first and second hooks 211 and 216 have different lengths corresponding to the shape of the discharge gasket 700.

That is, in the assembly process of the compressor, the end of the one side 250 of the valve casing 210 is adapted and fitted to a stepped portion 830 of the outlet 850 when assembling the valve casing 210. Then, when assembling the discharge gasket 700, one surface of the discharge gasket 700 presses the first hook 211 formed at the one side 250 of the valve casing 210 and the gasket block 710 presses the second hook 216 for arrangement.

In the above assembly process, both ends of the one side 250 of the valve casing 210 are naturally pressed and fixed by the discharge gasket 710, the gasket block 710, and the stepped portion 830. Therefore, the valve casing 210 can be prevented from being separated toward the discharge chamber 810 due to back pressure generated in the direction of the outlet 850 when the compressor is stopped.

The difference in height between the first hook 211 and the second hook 216 may be set in various manners according to the design specifications of the discharge gasket 700 and the gasket block 710.

The discharge valve 100 of the present disclosure may further include a recessed groove 220 and a sealing unit 600. The recessed groove 220 may be formed along the central circumference of the valve casing 210. The sealing unit 600 may be disposed in the recessed groove 220 to be pressed against the inner surface of the outlet 850, in order to prevent the leakage of a fluid to the gap between the valve casing 210 and the outlet 850.

Here, the sealing unit 600 may be made of an elastic material such as rubber or silicon. The sealing unit 600 may be an O-ring, but the present disclosure is not necessarily limited thereto. Of course, through the arrangement of the sealing unit 600 made of this material, the fixing force of the valve casing 210 onto the outlet 850 can be further enhanced by friction force.

The fluid compressed by the piston (not shown) of the compressor is introduced into the discharge chamber 810 through the discharge port 720, and then collected in the direction of the outlet 850 disposed on the discharge chamber 810 for discharge. In this case, a certain hydraulic pressure is required to push the core body 300 of the discharge valve 100, which is a force against the restoring force of the elastic body 400. When the required hydraulic pressure is formed, the fluid introduced through the first opening 230 while the core body 300 is pushed flows toward the outlet 850 by bypassing in the direction of the second opening 240.

When the compressed fluid is discharged, the hydraulic pressure is lowered again and the first opening 230 is closed while the core body 300 moves forward again by the restoring force of the elastic body 400.

Here, the fluid may flow back in the direction of the compressor due to back pressure since the pressure in a discharge pipe (not shown) is higher than that in the compressor when the compressor is stopped.

In the related art, the separation of the discharge valve due to back pressure is prevented by forcibly press-fitting a press-fitting portion, which is made of a metal material such as copper or aluminum, to a stepped portion. However, in the present disclosure, the overall valve casing 210 is made of a plastic material for cost reduction, and a press-fitting force is reduced by a change in the material.

The separation of the discharge valve may occur due to a back flow when press-fitting force is reduced. In order to complement this point, the valve casing 210 is disposed in such a manner that one end of the discharge valve is supported by the discharge gasket 700 and the sealing unit 600 is fitted to the stepped portion 830 of the outlet 850 as well. Through such a structure, the separation prevention effect can be maintained similar to the arrangement of the conventional press-fitting portion.

While the present disclosure has been described with respect to the specific embodiments of the compressor, it should be understood that this is intended to be exemplary only.

Accordingly, it will be understood by those skilled in the art that various variations and modifications may be made without departing from the spirit and scope of the disclosure as defined in the following claims.

INDUSTRIAL APPLICABILITY

The present disclosure relates to a discharge valve and a compressor having the same. 

1. A discharge valve for compressors, comprising: a valve casing having a hook formed around one side thereof such that the hook is seated on a discharge port of a rear housing, a first opening formed at a center of the one side for introduction of a compressed fluid, and a second opening formed around the other side thereof for discharge of the compressed fluid; a core body disposed within the valve casing; an elastic body disposed to touch one side of the core body; and a support block mounted to the other side of the valve casing to support the elastic body.
 2. The discharge valve according to claim 1, wherein the hook comprises: a first hook disposed around the one side of the valve casing; and a second hook disposed around the one side of the valve casing at a position facing the first hook.
 3. The discharge valve according to claim 2, wherein the first hook has a greater length than the second hook.
 4. The discharge valve according to claim 2, wherein the first and second hooks have different length.
 5. The discharge valve according to claim 2, wherein the first hook comprises: a first piece having a flat inner surface and a round outer surface; and a first support bar disposed between one surface of the valve casing and an inner surface of the first piece to support the first piece.
 6. The discharge valve according to claim 2, wherein the second hook comprises: a second piece having a flat inner surface and a round outer surface; and a second support bar disposed between one surface of the valve casing and an inner surface of the second piece to support the second piece.
 7. The discharge valve according to claim 1, further comprising: a recessed groove formed along a central circumference of the valve casing; and a sealing unit disposed in the recessed groove to be pressed against an inner surface of an outlet.
 8. The discharge valve according to claim 1, wherein the valve casing, the core body, and the support block are made of plastic.
 9. A compressor comprising: a valve plate provided with a discharge gasket having a discharge port through which a compressed fluid is discharged; a rear housing connected to the valve plate and having a discharge chamber connected to the discharge port; and a discharge valve disposed on the discharge chamber and comprising first and second hooks having different lengths corresponding to the shape of the discharge gasket. 